JP5845003B2 - Vertical axis fluid power generator - Google Patents

Description

  The present invention relates to a vertical axis fluid power generation apparatus, and more particularly to a vertical axis fluid power generation apparatus suitable for a wind power generation apparatus.

  For example, a wind power generator using a flow of wind (working fluid) has been developed as a vertical axis fluid power generator that generates power using a fluid flow. Such a vertical axis type wind turbine generator is arranged with a shaft body, a plurality of blades (windmills) connected to the shaft body, and a bearing, arranged at intervals around the central axis of the shaft body. A support body that rotatably supports the shaft body around a central axis, and a generator that generates electric power by converting mechanical energy obtained by rotating the shaft body in the circumferential direction into electric energy.

  For example, in the wind turbine generator described in Patent Document 1, a rotating mechanism (shaft) integrated with a vertical blade (blade) extends in a vertical direction (a direction perpendicular to a horizontal plane) with respect to the ground. In addition, a pair of bearings (bearings) are provided and are supported by an intermediate fixed shaft (support) in a state where they can be rotated.

JP 2006-207374 A

However, the conventional vertical axis hydroelectric generator has the following problems.
In other words, due to the movement of the working fluid and the weight of the blade and the shaft body, external forces in the radial direction intersecting the central axis direction of the shaft body and the thrust direction along the central axis direction act on the bearing. May not be sufficiently supported, and the shaft may not rotate smoothly due to vibrations generated in the apparatus.

In addition, it is difficult to set the coaxiality between the bearings with high accuracy, and when the accuracy of the coaxiality cannot be sufficiently ensured, the rotation center of the shaft body is likely to swing from the central axis of the shaft body. May not rotate smoothly.
In the fluid power generation device, it is not preferable that the shaft body does not rotate smoothly as described above because the power generation efficiency of the generator is reduced.

  This invention is made | formed in view of such a situation, Comprising: It aims at providing the vertical axis | shaft type fluid electric power generation apparatus which can rotate a shaft body smoothly and can improve electric power generation efficiency.

In order to achieve the above object, the present invention proposes the following means.
That is, the present invention provides a shaft body, a plurality of blades arranged at intervals around the central axis of the shaft body, and a plurality of blades connected to the one side along the central axis direction of the shaft body. and the arm is disposed on the other side along the central axis of the shaft body, and a generator for generating power by converting into electric energy mechanical energy which the shaft body is obtained by rotating in a circumferential direction, wherein A vertical shaft type hydroelectric power generator comprising: a support body that cantileverably supports the shaft body around the central axis via a bearing between the arm and the generator in a central axis direction of the shaft body an apparatus, wherein the bearing is a radial ball bearing single row, viewed including the angular contact ball bearing with double row, said the shaft body, the groove makes rolling the rolling elements of the angular contact ball bearing with double row Formed on the support, the angular ball shaft An outer ring of the angular ball bearing is provided opposite to the groove portion across the rolling element, the single-row radial ball bearing is disposed on the other side, and the double-row angular ball bearing is It is arranged on the one side .

  According to the vertical shaft type fluid power generation device of the present invention, the shaft body can be smoothly rotated to increase the power generation efficiency.

1 is an external view showing a vertical axis wind power generator according to a first embodiment of the present invention. It is a sectional side view which simplifies and shows the principal part of the vertical axis type wind power generator which concerns on 1st Embodiment of this invention. It is a sectional side view which shows the modification of FIG. It is a sectional side view which simplifies and shows the principal part of the vertical axis type wind power generator which concerns on 2nd Embodiment of this invention. It is a sectional side view which simplifies and shows the principal part of the vertical axis type wind power generator which concerns on 3rd Embodiment of this invention. It is a side view which shows the rotating shaft and support shaft of a vertical axis type wind power generator which concern on 3rd Embodiment of this invention. It is a sectional side view which shows the principal part of the vertical axis type wind power generator which concerns on 3rd Embodiment of this invention. It is a sectional side view which expands and shows the radial bearing vicinity in FIG. It is a sectional side view which expands and shows the angular bearing vicinity in FIG. It is a sectional side view which shows the modification of the principal part of 1st Embodiment shown by FIG. It is a sectional side view which shows the modification of the principal part of 1st Embodiment shown by FIG. It is a sectional side view which shows the modification of the principal part of 1st Embodiment shown by FIG. It is a sectional side view which shows the modification of the principal part of 1st Embodiment shown by FIG. It is a sectional side view which shows the modification of the principal part of 1st Embodiment shown by FIG. It is a figure which expands and shows the B section of FIG. It is a sectional side view which shows the modification of the principal part of 1st Embodiment shown by FIG.

(First embodiment)
As shown in FIGS. 1 and 2, a vertical axis wind power generator (vertical axis fluid power generator) 10 according to a first embodiment of the present invention includes a rotating mechanism that receives wind (working fluid) W and rotates. And a power generation mechanism that converts mechanical energy obtained by the rotation mechanism into electrical energy. The rotating mechanism is a rotating shaft (shaft body) 2 and a plurality of blades connected to the rotating shaft 2 while being arranged around the central axis C of the rotating shaft 2 as a component of the windmill 1. 1A and a casing (supporting body) 4 that supports the rotary shaft 2 so as to be rotatable around the central axis C via a bearing 3. The power generation mechanism includes a generator 5 that generates electric power by converting mechanical energy obtained by rotating the rotating shaft 2 in the circumferential direction (around the central axis C) into electric energy. The rotation mechanism and the power generation mechanism are disposed on an upper portion of a tower (post) 6 that stands on the ground F and extends in the vertical direction.

  The windmill 1 that receives the wind W has a rectangular plate shape or a band plate shape, and includes a plurality of blades 1A extending in the vertical direction with the ground F. These blades 1A are spaced evenly around the central axis C in the circumferential direction. Arranged. For this reason, the setting has no dependency on the wind direction, that is, the wind turbine 1 is set to have a shape capable of rotating around the central axis C of the rotation shaft 2 with respect to the wind W from any direction.

  Specifically, each blade 1 </ b> A is shaped to generate lift when receiving wind W, so that the wind turbine 1 rotates around the central axis C of the rotation shaft 2 by this lift.

Further, the rotary shaft 2 is arranged extending in the vertical direction so that the central axis C is perpendicular to the ground F. In FIG. 2, the rotating shaft 2 is made of a steel material and the like, for example, a first rotating member 11 integrated with the windmill 1 (blade 1 </ b> A) by bolting, welding, or the like, and a quenchable high carbon steel or the like. And a second rotating member 12 supported by the bearing 3. The lower end portion of the first rotating member 11 on the power generation mechanism (generator 5) side and the upper end portion of the second rotating member 12 are bolts and nuts (fitting by screw action) or the like at the connecting portion indicated by S in the drawing. Are connected in the direction of the central axis C.
In the above description, the first rotating member 11 and the second rotating member 12 are separate, but they may be integrated.

One end of an arm 1B having a rectangular plate shape or a band plate shape is connected to the outer peripheral surface of the first rotating member 11, and a plurality of radially outward projections are provided. These arms 1B are evenly arranged in the circumferential direction. They are arranged at intervals. The other end of the arm 1B is connected to the blade 1A. In the example shown in the figure, a pair of arms 1B supporting the blade 1A are provided so as to be separated from each other in the direction of the central axis C corresponding to one blade 1A.
The windmill 1 according to this embodiment is a so-called gyromill type windmill including a plurality of blades 1A that receive the wind W and a plurality of arms 1B that support the blades 1A.

The second rotating member 12 is rotatable with respect to the casing 4 by providing the bearings 3 in the vicinity of the upper end portion and in the vicinity of the lower end portion thereof. The bearing 3 includes radial bearings 13 that are separated from each other in the direction of the central axis C of the rotary shaft 2 and double-row angular bearings 14A and 14B. In the illustrated example, a radial bearing 13 is provided at the upper end of the second rotating member 12, and double-row angular bearings 14 </ b> A and 14 </ b> B are provided near the lower end of the second rotating member 12. Specifically, the radial bearing 13 is disposed on the wind turbine 1 side (one side) along the central axis C direction of the rotary shaft 2, and the double-row angular bearings 14 </ b> A and 14 </ b> B are along the central axis C direction of the rotary shaft 2. It is arrange | positioned at the edge part of the generator 5 side (other side).
Note that the vertical positions of the radial bearing 13 and the angular bearings 14A and 14B may be set opposite to the above. That is, the radial bearing 13 is disposed on the generator 5 side along the central axis C direction of the rotating shaft 2, and the angular bearings 14 </ b> A and 14 </ b> B are disposed on the windmill 1 side along the central axis C direction of the rotating shaft 2. Also good.

  In addition, the rolling surface on which the plurality of balls (rolling elements) 7 rolls is formed in the portion where the radial bearing 13 is provided in the second rotating member 12 and the portion where the double row angular bearings 14A and 14B are provided. Is provided.

  The radial bearing 13 includes a plurality of balls 7 that roll on the rolling surface of the second rotating member 12, and an annular outer ring 15 that abuts in the radial direction of the balls 7 and rolls the balls 7. ing. A first groove 16 for rolling the ball 7 is formed on the rolling surface of the second rotating member 12 corresponding to the radial bearing 13. The first groove portion 16 has an annular shape extending along the circumferential direction on the outer peripheral surface of the second rotating member 12, and has a concave curve shape that is recessed toward the central axis C side in a side sectional view of FIG. .

  The angular bearing 14A (14B) includes a plurality of balls 7 that roll on the rolling surface of the second rotating member 12, and an annular outer ring 17 that abuts in the radial direction of the balls 7 to roll the balls 7. have. In the illustrated example, the double-row angular bearings 14A and 14B are arranged back to back. Since the distances between the operating points of the angular bearings 14A and 14B can be set large by arranging them so as to be back-to-back in this way, the moment rigidity is increased. In addition, these angular bearings 14A and 14B may be set as front alignment or parallel alignment other than back alignment. In the illustrated example, the angular bearings 14A and 14B directly contact each other's outer rings 17 and 17 to apply a preload to the ball 7 by this contact. The preload may be applied by sandwiching a spacer or an elastic body between the bearings 14A and 14B.

  On the rolling surfaces corresponding to the double row angular bearings 14A and 14B of the second rotating member 12, double row second groove portions 18A and 18B for rolling the balls 7 in each row are formed. The second groove portions 18A and 18B have an annular shape extending along the circumferential direction on the outer peripheral surface of the second rotating member 12, and have a concave curve shape that is recessed toward the central axis C side in a side sectional view of FIG. ing.

  The code | symbol G in FIG. 2 has shown the partial cross section of the disk-shaped grindstone for grinding these 2nd groove parts 18A and 18B. On the outer peripheral surface of the grindstone G, there are formed convex portions GA and GB that protrude outward in the radial direction and have an annular shape extending along the circumferential direction and are spaced apart from each other in the axial direction. The protrusions GA and GB are set to have the same protruding height and shape from the outer peripheral surface. With such a grindstone G, the second groove portions 18A and 18B are ground into the same shape in the same process.

  In FIG. 1, the casing 4 has a multistage structure in which, for example, the upper portion 4 </ b> A on the windmill 1 side (one side) is reduced in diameter than the lower portion 4 </ b> B on the tower 6 side (the other side) opposite to the windmill 1. It has a cylindrical shape, and the lower end portion of the lower portion 4 </ b> B is connected to the upper end portion of the tower 6. In FIG. 2, an outer ring 15 of the radial bearing 13 is fixed to an upper end portion of the inner peripheral surface of the upper portion 4 </ b> A of the casing 4 so as to face the first groove portion 16 with the ball 7 of the radial bearing 13 interposed therebetween. Yes. Further, in the vicinity of the lower end portion on the inner peripheral surface of the upper portion 4A, the outer rings 17 of the angular bearings 14A and 14B are opposed to the second groove portions 18A and 18B across the balls 7 and 7 of the angular bearings 14A and 14B. 17 is fixed. Further, a generator 5, a control unit (not shown), and the like are accommodated in the lower portion 4 </ b> B of the casing 4.

  The generator 5 generates electric power by converting the rotational force (mechanical energy) obtained by the rotation of the rotary shaft 2 into electric energy. The generator 5 is connected to the lower end portion 4B of the casing 4 so as to surround the outer periphery of the magnet rotor 8 coupled to the lower end portion of the rotating shaft 2 in the radial direction and rotating together with the rotating shaft 2. The coil stator 9 is provided.

  When the windmill 1 receives the wind W and rotates around the central axis C of the rotation shaft 2, this rotation is transmitted to the magnet rotor 8 via the rotation shaft 2, and the magnet rotor 8 is coaxial with the windmill 1 and the rotation shaft 2. Rotate up. When the magnet rotor 8 rotates about the central axis C with respect to the coil stator 9, electromagnetic induction is generated between the magnet rotor 8 and the coil stator 9, and electric power is generated.

  As described above, according to the vertical axis wind power generator 10 according to the present embodiment, the rotation shaft 2 rotates about the central axis C of the rotation shaft 2 with respect to the casing 4 by providing the bearing 3. The bearing 3 includes a radial bearing 13 and double row angular bearings 14A and 14B. By providing the radial bearing 13 and the angular bearings 14A and 14B, the following effects can be obtained.

  That is, when the radial bearing 13 is provided as the bearing 3, when the external force is applied to the wind turbine 1 and the rotary shaft 2 in the horizontal direction (radial direction) intersecting the central axis C by receiving the wind W, the radial bearing 13 is provided. 13 can smoothly rotate the rotary shaft 2 while receiving the load with certainty. Further, by providing the angular bearings 14A and 14B as the bearing 3, the angular bearings 14A and 14B receive the above-described radial load, and the central axis C direction (thrust direction) generated by the own weight of the windmill 1 and the rotary shaft 2 or the like. ) Can be reliably received, and the rotating shaft 2 can be smoothly rotated.

  Further, since the angular bearings 14A and 14B are double-rowed, the angular bearings 14A and 14B are arranged in the thrust direction by combining the angular bearings 14A and 14B with the back-to-back alignment (DB structure) described in the present embodiment. The load on both sides (up and down) can be reliably received.

  Thus, since the bearing 3 (combination of the radial bearing 13 and the angular bearings 14A and 14B) of the present embodiment reliably receives the load in the radial direction and the thrust direction, it receives the wind W, the wind turbine 1 and the rotating shaft. The vibration due to the weight of 2 is reliably suppressed (absorbed), and the rotation of the rotating shaft 2 is smooth. Thereby, even if the air volume (wind speed) of the wind W that hits the windmill 1 is small, the windmill 1 and the rotary shaft 2 are easily rotated, so that the power generation efficiency of the vertical axis wind power generator 10 is increased. It is done.

  Further, since the radial bearing 13 and the angular bearings 14A and 14B are arranged apart from each other in the direction of the central axis C of the rotary shaft 2, the rotational center of the rotary shaft 2 is less likely to swing from the central axis C, and the rotation The rotation of the shaft 2 is performed more stably and with high accuracy.

  Further, on the outer peripheral surface of the rotary shaft 2, the first groove portion 16 which is a rolling surface for rolling the balls 7 of the radial bearing 13 and the rolling for rolling the balls 7 of the double row angular bearings 14 </ b> A and 14 </ b> B. Since the double-row second groove portions 18A and 18B, which are surfaces, are formed and the rotary shaft 2 and the bearing 3 are integrated, the following operational effects are obtained.

  That is, since the balls 7 of the radial bearing 13 and the balls 7 of the angular bearings 14A, 14B roll directly on the outer peripheral surface (rolling surface) of the rotating shaft 2, the radial bearing 13 and the angular bearings 14A, 14B The center of rotation of the rotary shaft 2 is accurately positioned so as to overlap the central axis C. Thereby, since rotation of the rotating shaft 2 becomes smooth, even if the air volume (wind speed) of the wind W which hits the windmill 1 is slight, the windmill 1 (and the rotating shaft 2) is easily rotated, and the power generation efficiency is improved. Enhanced.

  Specifically, for example, in a configuration in which the rotating shaft 2 is supported by the casing 4 via a pair of conventional bearings provided to be separated in the direction of the central axis C, the rotating shaft 2 portion and the casing 4 portion to which these bearings are attached. It was difficult to obtain the same degree of coaxiality between the bearings due to the machining error and assembly error (tilt, gap). On the other hand, in the vertical axis wind power generator 10 of the present embodiment, the first groove portion 16 and the second groove portions 18A and 18B for rolling the ball 7 are directly formed on the outer peripheral surface (rolling surface) of the rotating shaft 2. Therefore, the processing error and assembly error described above can be greatly reduced, and the coaxiality between the radial bearing 13 and the angular bearings 14A and 14B is set with high accuracy.

  In general, when a double-row angular bearing is used, it is difficult to accurately set the arrangement interval (the pitch between the balls 7 and 7 along the central axis C direction) between the rows of the angular bearing. That is, in the double-row angular bearing, the inner ring and the outer ring of each row are adjusted in the direction of approaching and separating from each other in the direction of the central axis C to adjust the preload on the ball 7. Roughness is eliminated to ensure rigidity and accuracy. However, this position adjustment is difficult, and when the arrangement interval is not determined to be a predetermined size, the preload on the ball 7 becomes insufficient or unstable, and the torque (rotational torque) for rotating the rotating shaft 2 increases. There was a thing. Such a large rotational torque is not preferable because it reduces the power generation efficiency of the vertical axis wind power generator.

  On the other hand, in the vertical axis wind power generator 10 of the present embodiment, the arrangement interval between the double row angular bearings 14A, 14B is more accurately determined by the double row second groove portions 18A, 18B formed directly on the rotary shaft 2. Since it is determined easily, it is easy to adjust the positions of the rows of the angular bearings 14A and 14B. Specifically, as described in the present embodiment, for example, by using the grindstone G that can grind the second groove portions 18A and 18B in the same process, the arrangement interval can be set with high accuracy and easily. Therefore, the precision of the preload with respect to the balls 7 in each row of the angular bearings 14A and 14B is ensured, the rotational torque is surely reduced, and the rotating shaft 2 is easily rotated, so that the power generation efficiency is increased.

  Further, since the rotary shaft 2 and the bearing 3 are integrated, the inner ring of the bearing 3 can be eliminated, so that the outer shape in the radial direction of the apparatus can be made compact and the cost is reduced.

  Further, in the vertical axis wind power generator 10, the rotating shaft 2 includes first and second rotating members 11 and 12 connected to each other in the central axis C direction. That is, in the rotating shaft 2, since the first and second rotating members 11 and 12 are manufactured as separate bodies and can be connected to each other, the first rotating member 11 that is preferably integrated with the windmill 1 is provided. The second rotating member 12 formed of a steel material that can be welded to the windmill 1 and the ball 7 of the bearing 3 directly rolls (that is, high hardness is desired) can be formed of quenchable high carbon steel or the like. Thereby, the 1st rotation member 11 and the windmill 1 can be firmly integrated, and the 1st groove part 16 and 2nd groove part 18A, 18B of the 2nd rotation member 12 are stable and highly accurate over a long period of time. Make a roll.

  Further, since the angular bearings 14A and 14B are disposed on the generator 5 side (the other side) in the direction of the central axis C in the rotating shaft 2, the angular bearings 14A and 14B are connected to the end portion (lower end portion) of the rotating shaft 2. ). Thereby, the following effects are obtained.

  That is, in general, the double-row angular bearing can receive a larger load than the radial bearing in the direction of the central axis C of the rotary shaft 2, so that the apparatus shown in FIG. As shown in the modification, it is conceivable that the shaft diameter of the rotary shaft 2 portion (lower end portion) where the angular bearings 14A and 14B are arranged is smaller than the shaft diameter of the other portions. The workability of the rotating shaft 2 is sufficiently ensured. Further, for example, the angular bearings 14A and 14B are disposed at the upper end portion and the central portion of the rotating shaft 2 (second rotating member 12) so that the portions corresponding to the angular bearings 14A and 14B have a smaller diameter than the other portions. In this case, the reduced diameter part partially constricts the rotary shaft 2, so that the rigidity of the rotary shaft 2 may not be sufficiently secured. On the other hand, according to the configuration of FIG. 3 described in the modification of the present embodiment (the lower end portion of the rotating shaft 2 is reduced in diameter), the rotating shaft 2 is not partially constricted, so that sufficient rigidity is ensured. The

  Further, in the vertical axis wind power generator 10 described in the present embodiment, the rotary shaft 2 is disposed so that the central axis C extends in a vertical direction perpendicular to the ground F, and the rotary shaft 2 and the windmill 1 Due to its own weight, the angular bearings 14A and 14B are always loaded in the direction of the central axis C. Further, the radial bearing 13 is loaded in the circumferential direction (radial direction) of the central axis C. By using the configuration of the bearing 3 of the present embodiment described above for such a vertical axis wind power generator 10, power can be generated stably and efficiently over a long period, which is more effective.

(Second Embodiment)
Next, a vertical axis wind power generator (vertical axis hydroelectric generator) 20 according to a second embodiment of the present invention will be described with reference to FIG. In addition, the same code | symbol is attached | subjected to the same member as above-mentioned embodiment, and the description is abbreviate | omitted.

  In the vertical axis wind power generator 20 of the present embodiment, the first groove portion 26 and the second groove portions 28A and 28B are formed in the casing 4 instead of being formed in the rotating shaft 2, and the like. Different from one embodiment.

  In this vertical shaft type wind power generator 20, as the bearing 3, a radial bearing 23 disposed at the upper end portion of the inner peripheral surface of the upper portion 4A of the casing 4 and the vicinity of the lower end portion of the inner peripheral surface are disposed. Double row angular bearings 24A, 24B. In addition, a rolling surface on which a plurality of balls (rolling elements) 7 rolls is formed in a portion where the radial bearing 23 is provided in the upper portion 4A of the casing 4 and a portion where the double row angular bearings 24A and 24B are provided. Each is provided.

  The radial bearing 23 has a plurality of balls 7 that roll on the rolling surface of the casing 4 and an annular inner ring 25 that abuts in the radial direction of the balls 7 and rolls the balls 7. A first groove portion 26 for rolling the ball 7 is formed on the rolling surface of the casing 4 corresponding to the radial bearing 23. The first groove portion 26 has an annular shape extending along the circumferential direction on the inner peripheral surface of the casing 4, and has a concave curve shape that is recessed toward the opposite side to the central axis C in a side sectional view of FIG. 4. Yes.

The angular bearing 24 </ b> A (24 </ b> B) has a plurality of balls 7 that roll on the rolling surface of the casing 4, and an annular inner ring 27 that contacts the balls 7 in the radial direction and rolls the balls 7. ing. In the illustrated example, the angular bearings 24A, 24B are combined in back-to-back alignment (DB structure), and a preload is applied to the ball 7 by bringing the inner rings 27, 27 into direct contact with each other.
In addition, these angular bearings 24A and 24B may be set as front alignment or parallel alignment other than back alignment.

  On the rolling surfaces corresponding to the double row angular bearings 24A, 24B of the casing 4, double row second groove portions 28A, 28B for rolling the balls 7 in each row are formed. The second groove portions 28A and 28B have an annular shape extending in the circumferential direction on the inner peripheral surface of the casing 4, and have a concave curve shape that is recessed toward the side opposite to the central axis C in the side sectional view of FIG. Has been.

The radial bearing 23 is disposed at the upper end portion of the second rotating member 12, and the inner ring 25 is fixed to the outer peripheral surface of the upper end portion. Specifically, the inner ring 25 of the radial bearing 23 is disposed to face the first groove portion 26 with the ball 7 of the radial bearing 23 interposed therebetween. Further, the angular bearings 24A and 24B are disposed in the vicinity of the lower end portion of the second rotating member 12, and the inner rings 27 and 27 are fixed to the outer peripheral surface in the vicinity of the lower end portion. Specifically, the inner rings 27, 27 of the angular bearings 24A, 24B are disposed to face the second groove portions 28A, 28B with the balls 7, 7 of the angular bearings 24A, 24B interposed therebetween.
Note that the vertical positions of the radial bearing 23 and the angular bearings 24A and 24B may be set opposite to the above. That is, the radial bearing 23 is disposed on the generator 5 side along the central axis C direction of the rotating shaft 2, and the angular bearings 24 </ b> A and 24 </ b> B are disposed on the windmill 1 side along the central axis C direction of the rotating shaft 2. Also good.

Also in the vertical axis wind power generator 20 of the present embodiment, the same operational effects as those of the vertical axis wind power generator 10 described above can be obtained.
That is, since the bearing 3 (the combination of the radial bearing 23 and the double row angular bearings 24A and 24B) reliably receives the load in the radial direction and the thrust direction, the bearing 3 receives the wind W, the weight of the windmill 1 and the rotating shaft 2, etc. Is reliably suppressed (absorbed) and the rotation of the rotary shaft 2 is smooth. Thereby, even if the air volume (wind speed) of the wind W that hits the windmill 1 is small, the windmill 1 and the rotary shaft 2 are easily rotated, so that the power generation efficiency of the vertical axis wind power generator 20 is increased. It is done.

  Further, on the inner peripheral surface of the casing 4, a first groove portion 26 that is a rolling surface for rolling the ball 7 of the radial bearing 23 and a rolling for rolling each ball 7 of the double row angular bearings 24 </ b> A and 24 </ b> B. Since the double-row second groove portions 28A and 28B, which are surfaces, are formed and the casing 4 and the bearing 3 are integrated, the following operational effects can be obtained.

  That is, since the balls 7 of the radial bearing 23 and the balls 7 of the angular bearings 24A, 24B roll directly on the inner peripheral surface (rolling surface) of the casing 4, the radial bearing 23 and the angular bearings 24A, 24B The center of rotation of the rotary shaft 2 is accurately positioned so as to overlap the central axis C. Thereby, since rotation of the rotating shaft 2 becomes smooth, even if the air volume (wind speed) of the wind W which hits the windmill 1 is slight, the windmill 1 (and the rotating shaft 2) is easily rotated, and the power generation efficiency is improved. Enhanced.

In the vertical axis wind power generator 20 of the present embodiment, since the ball 7 does not roll on the outer peripheral surface of the rotating shaft 2 as in the above-described embodiment, the second rotating member 12 is made of high carbon hard or the like. Instead of using steel, a steel material or the like may be used. In this case, the entire rotating shaft 2 may be integrally formed of a steel material or the like.
Further, without using the inner ring 25 of the radial bearing 23 and the inner ring 27 of the angular bearings 24A and 24B, the first groove portion 16 and the second groove portion which are the rolling surfaces described in the first embodiment on the outer peripheral surface of the rotating shaft 2. 18A and 18B may be formed, and the inner and outer rings of the radial bearing 23 and the angular bearings 24A and 24B may be deleted. In this case, the outer shape (diameter) of the device becomes more compact, and further cost reduction is possible. Specifically, the first groove portion and the second groove portion of the present invention are formed in at least one of the rotating shaft 2 and the casing 4 (that is, the rotating shaft 2 and / or the casing 4).

(Third embodiment)
Next, a vertical axis wind power generator (vertical axis hydroelectric generator) 30 according to a third embodiment of the present invention will be described with reference to FIGS. In addition, the same code | symbol is attached | subjected to the same member as above-mentioned embodiment, and the description is abbreviate | omitted.

  As shown in FIG. 5, in the vertical shaft type wind power generator 30 of the present embodiment, the rotating shaft (shaft body) 32 has a hollow shaft shape (tubular shape), and is accommodated coaxially within the rotating shaft 32. The support shaft (support body) 31 supports the rotary shaft 32 via the bearing 3 so as to be rotatable around the central axis C of the rotary shaft 32 from the central axis C side (inside in the radial direction). An arm 1 </ b> B of the windmill 1 projects from the outer peripheral surface of the rotating shaft 32. A magnet rotor 8 is disposed at the lower end (in the radial direction) of the rotating shaft 32.

  The lower end portion of the support shaft 31 is supported by a support base 39 having a larger diameter than the support shaft 31, and the lower end portion of the support base 39 is connected to the upper end portion of the tower 6 (not shown). A coil stator 9 is disposed on the upper surface of the support base 39 so as to surround the magnet rotor 8. And the generator 5 provided with the magnet rotor 8 and the coil stator 9 is formed. In the example of FIG. 5, the support shaft 31 is formed in a solid shaft shape, and in the examples shown in FIGS. 6 to 9, the support shaft 31 is formed in a hollow shaft shape (tubular shape). .

The rotation shaft 32 is rotatable with respect to the support shaft 31 by providing the bearings 3 in the vicinity of the upper end portion and in the vicinity of the lower end portion on the inner peripheral surface thereof. The bearing 3 includes radial bearings 33 that are separated from each other in the direction of the central axis C of the rotary shaft 32 and double-row angular bearings 34A and 34B. In the illustrated example, a radial bearing 33 is provided at the upper end of the rotating shaft 32, and double-row angular bearings 34 </ b> A and 34 </ b> B are provided near the lower end of the rotating shaft 32.
Note that the vertical positions of the radial bearing 33 and the angular bearings 34A, 34B may be set opposite to the above. That is, the angular bearings 34 </ b> A and 34 </ b> B may be provided at the upper end portion of the rotating shaft 32, and the radial bearing 33 may be provided near the lower end portion of the rotating shaft 32.

  In addition, a rolling surface on which a plurality of balls 7 rolls is formed between a portion where the radial bearing 33 is provided on the support shaft 31 and a portion where the double-row angular bearings 34A and 34B of back-to-back (DB structure) are provided. Each is provided.

  The radial bearing 33 has a plurality of balls 7 that roll on the rolling surface of the support shaft 31 and an annular outer ring 35 that abuts in the radial direction of the balls 7 and rolls the balls 7. . The outer ring 35 is fixed to the upper end portion of the inner peripheral surface of the rotating shaft 32. A first groove 36 for rolling the ball 7 is formed on the rolling surface of the support shaft 31 corresponding to the radial bearing 33. The first groove portion 36 has an annular shape extending along the circumferential direction on the outer peripheral surface of the support shaft 31, and has a concave curve shape that is recessed toward the central axis C side in a side sectional view of FIG. The outer ring 35 of the radial bearing 33 is disposed to face the first groove portion 36 with the ball 7 of the radial bearing 33 interposed therebetween. When the ball 7 is filled (inserted) into the radial bearing 33 during manufacturing, the ball 7 may be inserted from the rolling element insertion portion 32A that can be opened and closed on the outer peripheral surface of the rotating shaft 32 in FIG. .

  The angular bearing 34 </ b> A (34 </ b> B) has a plurality of balls 7 that roll on the rolling surface of the support shaft 31 and an annular outer ring 37 that abuts the balls 7 in the radial direction and rolls the balls 7. doing. The outer ring 37 is fixed near the lower end portion of the inner peripheral surface of the rotating shaft 32. In the example of FIG. 5, the double row angular bearings 34 </ b> A and 34 </ b> B are arranged in contact with each other for back-to-back alignment. In the example of FIGS. 6 to 9, a spacer 40 is disposed between the double row angular bearings 34 </ b> A and 34 </ b> B combined for back-to-back alignment, and this spacer 40 preloads the balls 7 and 7 in each row. It is trying to grant.

  In addition, on the rolling surfaces corresponding to the double row angular bearings 34A, 34B of the support shaft 31, double row second groove portions 38A, 38B for rolling the rows 7 of balls 7 are formed. The second groove portions 38A and 38B have an annular shape extending in the circumferential direction on the outer peripheral surface of the support shaft 31, and have a concave curve shape that is recessed toward the central axis C side in a side sectional view of FIG. . The outer rings 37, 37 of the angular bearings 34A, 34B are arranged to face the second groove portions 38A, 38B across the balls 7, 7 of the angular bearings 34A, 34B. During filling, when the ball 7 is filled (inserted) into the angular bearing 34A (34B), the ball 7 is inserted downward (upward) from the gap between the outer ring 37 and the support shaft 31 in FIG. That's fine.

  When the windmill 1 receives the wind W and rotates around the central axis C of the rotation shaft 32, this rotation is transmitted to the magnet rotor 8 through the rotation shaft 32, and the magnet rotor 8 is coaxial with the windmill 1 and the rotation shaft 32. Rotate up. When the magnet rotor 8 rotates about the central axis C with respect to the coil stator 9, electromagnetic induction is generated between the magnet rotor 8 and the coil stator 9, and electric power is generated.

Also in the vertical axis wind power generator 30 of the present embodiment, the same effects as those of the vertical axis wind power generators 10 and 20 described above can be obtained.
Moreover, in the vertical axis wind power generator 30 of this embodiment, since the moment added to the bearing 3 becomes small, the radial load by a moment becomes small.

The present invention is not limited to the embodiment described above, and various modifications can be made without departing from the spirit of the present invention.
For example, in the above-described embodiment, the vertical axis wind power generators 10, 20, and 30 that rotate the windmill 1 using the wind W as the working fluid have been described as the vertical axis fluid power generator, but the present invention is not limited thereto. It may be a vertical axis hydroelectric generator that rotates water turbine (impeller) using water as a working fluid.

  In the above-described embodiment, the radial bearing of the bearings 3 is arranged on the upper side (one side) of the rotation shafts 2 and 32 in the direction of the central axis C, and the double-row angular bearings are the central axes of the rotation shafts 2 and 32. Although it has been arranged on the lower side (the other side) in the C direction, it is not limited to this. In other words, the double-row angular bearings may be arranged on the upper side in the central axis C direction of the rotary shafts 2 and 32, and the radial bearings may be arranged on the lower side in the central axis C direction of the rotary shafts 2 and 32.

  Further, although the balls 7 are used as the rolling elements of the bearing 3, the present invention is not limited to this. For example, rollers or the like may be used as the rolling elements of the bearing 3.

  Further, the vertical axis wind power generator is not limited to the gyromill type. That is, other Darrieus type, straight wing type, Savonius type, paddle type, cross flow type, S type rotor type and the like may be used.

In addition, the following modification may be used instead of the configuration of the first embodiment described with reference to FIG.
10 to 16 show a modification of the first embodiment. In addition, the same code | symbol is attached | subjected to the same member as 1st Embodiment, and the description is abbreviate | omitted.

  As described with reference to FIG. 2, a rolling surface (groove portion) on which the ball 7 of the bearing 3 rolls is formed on the outer peripheral surface of the rotating shaft 2, and the rotating shaft 2 and the bearing 3 are configured integrally. For this, it is necessary to insert the ball 7 between the rotary shaft 2 and the outer ring from the state where the rotary shaft 2 is loosely inserted into the outer ring of the bearing 3. In order to insert the balls 7 into the double row angular bearings 14A, 14B, for example, it is conceivable to form a ball insertion hole penetrating in the outer ring 17 in the radial direction. However, in this case, since the ball insertion hole is opened in the rolling surface of the outer ring 17, there is a possibility that the rolling of the ball 7 is hindered or the outer ring 17 is damaged. Therefore, the configuration shown in FIG. 10 may be used for the purpose of smoothly rolling the ball 7 with high accuracy and preventing the outer ring 17 from being damaged.

  In the example shown in FIG. 10, the second rotating member 12 of the rotating shaft 2 is formed with a single row of second groove portions 50 for rolling the balls 7 of the double row of angular bearings 14A, 14B. The second groove portion 50 is recessed from the outer surface of the rotating shaft 2 and has an annular shape extending in the circumferential direction, and the width in the central axis C direction is set so as to correspond to the double-row angular bearings 14A and 14B. And wider than the second groove portions 18A and 18B described above. In addition, the 2nd groove part 50 is good also as a double row like the example demonstrated in FIG.

  A rolling surface 50A having a circular arc cross section for rolling the ball 7 of the angular bearing 14A is formed at one end portion (upper end portion in FIG. 10) along the central axis C direction of the second groove portion 50. The rolling surface 50A is disposed opposite to the rolling surface of the outer ring 17 of the angular bearing 14A with the ball 7 interposed therebetween. Further, a rolling surface 50B having an arcuate cross section for rolling the ball 7 of the angular bearing 14B is formed at the other end portion (the lower end portion in FIG. 10) of the second groove portion 50 along the central axis C direction. The rolling surface 50B is disposed opposite to the rolling surface of the outer ring 17 of the angular bearing 14B with the ball 7 interposed therebetween.

  The rolling surface 50A and the rolling surface 50B are smoothly connected to each other via the bottom surface 50C of the second groove portion 50 located between them. Specifically, the depth of the bottom surface 50C (the distance recessed from the outer surface of the rotating shaft 2), the depth of the deepest portion of the rolling surface 50A, and the depth of the deepest portion of the rolling surface 50B are the same. .

  The outer ring 15 of the radial bearing 13 and the outer ring 17 of the angular bearings 14A and 14B are in contact with the inner surface of a cylindrical housing (support) 51 from the outside in the radial direction, and the radial bearing 13 and the angular bearing 14A, 14 </ b> B is supported between the radially inner rotating shaft 2 and the radially outer housing 51. The rotary shaft 2 can rotate around the central axis C with respect to the housing 51 via the radial bearing 13 and the angular bearings 14A and 14B, and the sliding movement in the direction of the central axis C is restricted.

  Of the inner surface of the housing 51, a portion that contacts the outer ring 15 of the radial bearing 13 (an upper portion of the housing 51 in FIG. 10, hereinafter referred to as a radial bearing contact portion) 51A is a portion that contacts the outer ring 17 of the angular bearings 14A and 14B. (A lower portion of the housing 51 in FIG. 10, hereinafter referred to as an angular bearing contact portion) 51B is formed to protrude radially inward. Further, one side (upper side in FIG. 10) of the angular bearing contact portion 51B on the inner surface of the housing 51 faces the other side (lower side in FIG. 10), and one end surface (upper side) of the outer ring 17 of the angular bearing 14A. An end face 51 </ b> C that abuts the end face is formed.

  A bearing pressing member 52 is disposed on the other side of the angular bearing 14 </ b> B between the rotating shaft 2 and the housing 51. The bearing pressing member 52 has an annular plate-shaped base portion 52A and a cylindrical pressing portion 52B standing from one end surface of the base portion 52A. The bearing pressing member 52 is detachably fixed to the housing 51 with a bolt or the like, and one end surface of the pressing portion 52B of the bearing pressing member 52 is in contact with the other end surface (lower end surface) of the outer ring 17 of the angular bearing 14B. . Further, a slight gap is provided between the inner peripheral surface facing radially inward in the base portion 52 </ b> A of the bearing pressing member 52 and the outer peripheral surface of the rotating shaft 2.

  In this modification, a spacer 53 is disposed between the outer rings 17 of the double row angular bearings 14A, 14B. The spacer 53 has, for example, an annular plate shape as a whole, can be divided in the circumferential direction, or can be deformed in the radial direction (for example, can be opened and closed via a hinge portion so as to open a part in the circumferential direction). And is detachably disposed between the outer rings 17.

  In this modification, the ball 7 is inserted into the angular bearings 14A and 14B in the following procedure. That is, the outer ring 17 is centered in the state where the housing 51 is not disposed radially outward of the outer ring 17 of the angular bearings 14A and 14B and the spacer 53 is not disposed between the outer rings 17. While moving in the direction of the axis C, a gap is provided between the rolling surface of the outer ring 17 and the rolling surface 50A or the rolling surface 50B of the second groove 50 so that the ball 7 can be inserted from the outside.

  Next, the ball 7 is inserted through the gap, the outer ring 17 is slid in the direction of the central axis C, and the gap is narrowed so that the ball 7 is accommodated between the rolling surfaces. When the balls 7 are thus inserted into the angular bearings 14A and 14B, the spacers 53 are mounted between the outer rings 17 of the angular bearings 14A and 14B.

  Next, while sliding the housing 51 toward the other side along the direction of the central axis C with respect to the rotating shaft 2, the inner surface of the housing 51 is moved to the outer ring 15 of the radial bearing 13 and the outer ring 17 of the angular bearings 14A and 14B. The radial bearing 13 and the angular bearings 14 </ b> A and 14 </ b> B are supported between the rotating shaft 2 and the housing 51 by contacting each other. As a result, the outer side of the spacer 53 in the radial direction is covered with the housing 51, and the spacer 53 is restricted from falling out from between the outer rings 17 to the outer side in the radial direction. Further, when the housing 51 is slid toward the other side, the end surface 51C of the housing 51 and the one end surface of the outer ring 17 of the angular bearing 14A are brought into contact with each other and further toward the other side. The sliding movement of the housing 51 is restricted.

  Next, the bearing pressing member 52 is inserted between the rotary shaft 2 and the housing 51 toward one side in the direction of the central axis C, and one end surface of the pressing portion 52B of the bearing pressing member 52 and the angular bearing 14B are inserted. The bearing pressing member 52 is fixed to the housing 51 in a state where the other end surface of the outer ring 17 is in contact with the outer ring 17.

  Thus, the outer ring 17 of the angular bearing 14A is brought into contact with the end surface 51C of the housing 51 from one side in the central axis C direction, and the outer ring 17 of the angular bearing 14B is brought into contact with the bearing holding member 52 from the other side in the central axis C direction. The outer rings 17 of the angular bearings 14A and 14B are maintained close to each other with the spacer 53 interposed therebetween, and are relatively in the direction of the central axis C. Movement is restricted.

  According to the modification of FIG. 10 described above, the ball 7 is inserted by sliding the outer ring 17 of the double row angular bearings 14A, 14B in the direction of the central axis C with respect to the first groove 50 of the rotary shaft 2. Therefore, it is not necessary to form a ball insertion hole in the outer ring 17. That is, since it can form smoothly without producing a level | step difference in the rolling surface of the outer ring | wheel 17, the ball | bowl 7 can be rolled smoothly and accurately, and the failure | damage of the outer ring | wheel 17 can be prevented. Moreover, according to this structure, the workability of assembly is good.

  In the case where the radial bearing contact portion 51A and the angular bearing contact portion 51B are formed on the inner surface of the housing 51 as in the example described with reference to FIG. 10, these contact portions 51A and 51B are formed in the same process. Although it is possible to obtain the coaxiality between the contact portions 51A and 51B by processing, the coaxiality between the radial bearing 13 and the angular bearings 14A and 14B depends on the processing accuracy of each component. It is difficult to ensure accuracy. Further, the coaxiality between the bearings 3 cannot be adjusted during assembly. Therefore, for the purpose of accurately setting the coaxiality of the radial bearing 13 and the angular bearings 14A and 14B, a configuration as shown in FIG. 11 may be adopted.

  In the example shown in FIG. 11, the housing 51 is divided in the direction of the central axis C and is composed of a plurality of members. Specifically, the housing 51 includes a cylindrical radial bearing support portion 54 in which a radial bearing contact portion 51A is formed on the inner surface, and a cylindrical angular bearing support portion 55 in which an angular bearing contact portion 51B is formed on the inner surface. And have.

  An annular flange 54A that protrudes radially outward and extends in the circumferential direction is formed at the other end of the radial bearing support portion 54. In addition, an annular flange 55A that protrudes radially outward and extends along the circumferential direction is formed at one end of the angular bearing support portion 55. The flanges 54A and 54B are connected to each other by a connecting member such as a bolt, whereby the radial bearing support portion 54 and the angular bearing support portion 55 are integrally connected.

  In this modification, the radial bearing support portion 54 and the angular bearing support portion 55 are coupled so as to be relatively movable at least in the radial direction. That is, in FIG. 11, the angular bearing support portion 55 is movable in the radial direction indicated by the reference symbol A <b> 1 with respect to the radial bearing support portion 54, whereby the radial bearing support portion 54, the angular bearing support portion 55, and the like. The relative position in the A1 direction (radial direction) can be adjusted.

  Further, a spacer is interposed between the other end surface of the radial bearing support portion 54 and the one end surface of the angular bearing support portion 55, or the distance between these end surfaces can be adjusted by a screw action. The relative positions of the 55 in the direction of the central axis C may be adjustable. In this case, the angular bearing support portion 55 is movable with respect to the radial bearing support portion 54 in, for example, an inclination direction indicated by reference numeral A2.

  According to the modified example of FIG. 11 described above, the radial relative position between the radial bearing contact part 51A and the angular bearing contact part 51B can be adjusted. The coaxiality between the bearing 13 and the angular bearings 14A and 14B can be set (adjusted) with high accuracy. In addition, since the coaxiality between the bearings 3 is ensured with high accuracy, the eccentric load is reduced, and the rotating shaft 2 is easily rotated smoothly, thereby improving the power generation efficiency.

  Further, the vertical axis wind power generator 10 is installed in the field where natural wind W is easily received, and there is a risk that dust or the like may adhere to the ball 7 or the rolling surface of the bearing 3. Further, grease may leak from the bearing 3 to the outside. Therefore, for the purpose of preventing dust and the like from adhering to the ball 7 and the rolling surface of the bearing 3 and preventing grease leakage from the bearing 3, a configuration as shown in FIG.

  In the example shown in FIG. 12, an annular seal attachment groove 57 </ b> A that is recessed from the outer peripheral surface and extends along the circumferential direction is formed on the other side of the second groove portion 50 in the central axis C direction on the outer peripheral surface of the rotating shaft 2. Has been. The seal attachment groove 57 </ b> A is disposed close to the second groove portion 50. Further, in the inner peripheral surface of the pressing portion 52B of the bearing pressing member 52, a portion located on the other side in the central axis C direction from the seal mounting groove 57A is recessed from the inner peripheral surface and extends in the circumferential direction. A seal mounting groove 57B is formed.

  In this modification, a seal member 56 is disposed between the housing 51 and the rotary shaft 2 so as to cover the ball 7 of the bearing 3 from the direction of the central axis C. Specifically, annular seal members 56A and 56B are arranged between the bearing pressing member 52 of the housing 51 and the rotary shaft 2 so as to cover the ball 7 of the angular bearing 14B from the other side in the central axis C direction. It is installed.

  The radially inner portion of the seal member 56A is inserted into the seal attachment groove 57A. The radially outer portion of the seal member 56B is inserted into the seal attachment groove 57B. The radially outer portion of the seal member 56A and the radially inner portion of the seal member 56B are disposed so as to overlap with each other in the central axis C direction. These seal members 56A and 56B are configured to bypass the one side space (space on the bearing 3 side) and the other side space (external space) of the seal members 56A and 56B between the rotary shaft 2 and the housing 51. Thus, a labyrinth structure (a detour structure) including the seal member 56 is configured.

12, the seal members 56A and 56B are disposed between the housing 51 and the rotary shaft 2 so as to partition the ball 7 and the rolling surface of the bearing 3 from the outside. Therefore, it is possible to prevent dust and the like from entering from the outside and adhere to the ball 7 and the rolling surface. Therefore, the ball 7 rolls stably, the rotating shaft 2 is easy to turn smoothly, and the power generation efficiency is improved. Further, since the seal members 56A and 56B are provided, the grease is prevented from leaking to the outside from the bearing 3, so that the bearing 3 operates stably over a long period of time and the maintenance becomes simple.
Further, by providing the labyrinth structure described above, the dustproof effect is sufficiently enhanced and the effect of preventing grease leakage is improved.

  In the illustrated example, the seal members 56A and 56B are disposed so as to cover the ball 7 of the angular bearing 14B from the other side in the direction of the central axis C. However, the present invention is not limited to this. 56A and 56B may be arrange | positioned so that the ball | bowl 7 of the radial bearing 13 may be covered from the one side of the central axis C direction. Further, the number of the seal members 56 is not limited.

  Further, in the first embodiment described with reference to FIG. 2, the rotating shaft 2 includes a first rotating member 11 made of steel or the like and integrated with the windmill 1, and a first rotating member 11 made of high carbon steel or the like and supported by the bearing 3. However, the present invention is not limited to this, and the following modifications shown in FIGS. 13 to 16 may be used.

  In FIG. 2, the entire second rotating member 12 of the rotating shaft 2 having a solid bar shape is formed of high carbon steel. This is because the rotating shaft 2 requires hardness on the rolling surface on which the ball 7 of the bearing 3 rolls. However, high carbon steel is expensive, and the production cost of the rotating shaft 2 increases. Therefore, for the purpose of reducing the manufacturing cost of the rotary shaft 2 while the ball 7 of the bearing 3 rolls on the rolling surface of the rotary shaft 2 with high accuracy, the configuration shown in FIG.

  In the example shown in FIG. 13, the rotating shaft 2 has a hollow pipe shape. The rotating shaft 2 has a rolling part 59 and a connecting part 60 that are connected in the direction of the central axis C by a welded part 58. The rolling part 59 is made of a carburized material such as SCM420, for example, and is formed by carburizing and quenching after the welded part 58 is carburized. The rolling part 59 is formed with a first groove part 16 or a second groove part 18A, 18B having a rolling surface between both ends of the outer peripheral surface in the direction of the central axis C. The connection part 60 consists of steel materials, such as STKM, for example, and the rolling surface is not formed in the outer peripheral surface.

  According to the modification of FIG. 13, a portion of the rotating shaft 2 other than the rolling surface on which the ball 7 of the bearing 3 rolls can be an inexpensive connecting portion 60 made of steel. That is, the rolling surface on which the ball 7 of the bearing 3 rolls is formed with high hardness, and while the smooth rolling of the ball 7 is ensured, many parts of the rotating shaft 2 can be made of steel, thereby reducing costs. An effect is obtained.

  In the example described with reference to FIG. 13, since the rolling part 59 and the connection part 60, which are different from each other, are welded and connected by the welding part 58, it is difficult to ensure the strength of the welding part 58. Specifically, since the rolling part 59 made of high carbon steel has a large carbon content, it is difficult to ensure the strength by welding. For this reason, the ball 7 of the bearing 3 rolls on the rolling surface of the rotary shaft 2 with high accuracy, the rotary shaft 2 can be manufactured at low cost, and the strength of the rotary shaft 2 is ensured. It is good also as a structure like 15.

  In the example shown in FIGS. 14 and 15, both the rolling part 59 and the connecting part 60 of the rotary shaft 2 are made of steel such as STKM. A ceramic film (high hardness film) 61 made of, for example, silicon nitride is formed on the inner surface of the first groove portion 16 or the second groove portions 18A and 18B in the rolling portion 59. The ceramic film 61 is formed, for example, by thermal spraying on the first groove portion 16 or the second groove portions 18A and 18B.

  14 and 15, parts of the rotating shaft 2 other than the rolling surface on which the ball 7 of the bearing 3 rolls can be made of an inexpensive steel material. That is, the rolling surface on which the ball 7 of the bearing 3 rolls is formed of a ceramic film 61 having a high Young's modulus, and while the smooth rolling of the ball 7 is ensured, most of the other rotating shaft 2 is made of steel. Can be manufactured with a cost reduction effect. Furthermore, since both the rolling part 59 and the connection part 60 are made of steel, the strength of the welded part 58 is sufficiently secured and the strength of the rotating shaft 2 is secured.

  For the purpose of performing the rolling of the ball 7 of the bearing 3 with higher accuracy, increasing the strength of the rotating shaft 2 and improving the productivity, the example shown in FIG. It is good also as a structure.

  In the example shown in FIG. 16, the rotating shaft 2 does not have the rolling part 59 and the connecting part 60 connected by the weld part 58. That is, the entire rotating shaft 2 is integrally formed of a steel material. The ceramic film 61 is sprayed on the inner surface of the first groove portion 16 or the second groove portions 18A and 18B formed on the outer peripheral surface of the rotating shaft 2.

  According to the modification of FIG. 16, the ball 7 of the bearing 3 can be rolled with higher accuracy while obtaining the same effect as that of the modification of FIG. 14 described above (the radial bearing 13 and the angular bearing 14A). 14B), the strength of the rotating shaft 2 can be increased, and the productivity can be improved.

  In addition, you may combine suitably the component demonstrated in the above-mentioned embodiment and modification of this invention. In addition, the above-described components can be replaced with well-known components without departing from the spirit of the present invention.

DESCRIPTION OF SYMBOLS 1 ... Windmill, 1A ... Blade, 2, 32 ... Rotary shaft (shaft body), 3 ... Bearing, 4 ... Casing (support body), 5 ... Generator, 7 ... Ball (rolling body), 10, 20, 30 ... Vertical shaft type wind power generation device (vertical shaft type fluid power generation device), 13, 23, 33 ... radial bearing, 14A, 14B, 24A, 24B, 34A, 34B ... angular bearing, 16, 26, 36 ... first groove, 18A , 18B, 28A, 28B, 38A, 38B, 50 ... second groove portion, 31 ... support shaft (support), 51 ... housing (support), C ... central shaft, W ... wind (working fluid).

Claims (1)

A shaft,
A plurality of blades arranged at intervals around the central axis of the shaft body;
A plurality of arms connecting the plurality of blades on one side along the central axis direction of the shaft body;
A generator that is disposed on the other side along the central axis direction of the shaft body and converts the mechanical energy obtained by rotating the shaft body in the circumferential direction into electric energy to generate electric power;
A vertical shaft fluid comprising: a support body that cantileverably supports the shaft body around the central axis via a bearing between the arm and the generator in the central axis direction of the shaft body A power generator,
The bearing includes a radial ball bearing of a single row, the angular contact ball bearing with double row, only including,
The shaft body is formed with a groove for rolling the rolling elements of the double-row angular ball bearing,
The support body is provided with an outer ring of the angular ball bearing so as to face the groove portion across the rolling element of the angular ball bearing,
The single-row radial ball bearing is disposed on the other side,
The vertical axis type fluid power generation device according to claim 1, wherein the double-row angular ball bearings are disposed on the one side .

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